US11168672B2 - Mounting of an intermediate shaft in particular of a wind gearbox - Google Patents
Mounting of an intermediate shaft in particular of a wind gearbox Download PDFInfo
- Publication number
- US11168672B2 US11168672B2 US16/616,290 US201816616290A US11168672B2 US 11168672 B2 US11168672 B2 US 11168672B2 US 201816616290 A US201816616290 A US 201816616290A US 11168672 B2 US11168672 B2 US 11168672B2
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- bearing
- shaft end
- gearbox
- shaft
- axial
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
- F16C17/08—Sliding-contact bearings for exclusively rotary movement for axial load only for supporting the end face of a shaft or other member, e.g. footstep bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
- F16C17/24—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with devices affected by abnormal or undesired positions, e.g. for preventing overheating, for safety
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/26—Systems consisting of a plurality of sliding-contact bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/02—Sliding-contact bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/103—Construction relative to lubrication with liquid, e.g. oil, as lubricant retained in or near the bearing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D15/00—Transmission of mechanical power
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
- F03D80/70—Bearing or lubricating arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2240/00—Components
- F05B2240/50—Bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2260/00—Function
- F05B2260/40—Transmission of power
- F05B2260/403—Transmission of power through the shape of the drive components
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2260/00—Function
- F05B2260/40—Transmission of power
- F05B2260/403—Transmission of power through the shape of the drive components
- F05B2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
- F05B2260/40311—Transmission of power through the shape of the drive components as in toothed gearing of the epicyclic, planetary or differential type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/31—Wind motors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02039—Gearboxes for particular applications
- F16H2057/02078—Gearboxes for particular applications for wind turbines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
Definitions
- the invention relates to a mounting of an intermediate shaft of a gearbox, in particular of a wind gearbox, that is of a gearbox for a wind power plant and an operating method.
- Gearboxes can be employed in various applications. Gearboxes are thus used, for example, in maritime drive systems, but also in wind power plants or in other industrial areas of application.
- the gearbox is for example a spur gear unit, which in particular has helical teeth.
- a gearbox has in particular an intermediate shaft, wherein this shaft for example takes the form of a two-stage spur gear part Planetary gears too can for example be employed in wind power plants.
- a solution to the problem emerges from a mounting of an intermediate shaft of a gearbox, wherein the intermediate shaft has a first shaft end and a second shaft end, wherein there is a gear element between the first shaft end and the second shaft end, wherein a first radial bearing is at the first shaft end, wherein a second radial bearing is at the second shaft end, wherein a first axial bearing is at the first shaft end and a second axial bearing is at the second shaft end.
- a wind gearbox as including a mounting as set forth above.
- the problem is solved by a method for operating a wind gearbox as set forth above, wherein a compression time of the reversing bearing is selected that corresponds to a frequency of a change in load.
- a mounting of an intermediate shaft of a gearbox has the intermediate shaft, wherein the intermediate shaft has a first shaft end and a second shaft end, wherein at least one gear element is located between the first shaft end and the second shaft end.
- the gear element is for example a gear wheel located on the intermediate shaft or a sprocket, etc. integrated into the shaft.
- there is a first radial bearing at the first shaft end and a second radial bearing for the second shaft end wherein there is also a first axial bearing on the first shaft end and a second axial bearing on the second shaft end.
- On the shaft end means in the area of the end of the shaft, wherein this end area can intersect axially with the shaft, but can also extend beyond the axial expansion of the shaft.
- the radial bearing at least predominantly takes up forces that run radially.
- the axial bearing at least predominantly takes up forces that run axially.
- a shaft can be prevented from performing axial movements in an impermissible manner.
- axial forces can arise which are to be absorbed by an axial bearing.
- Bearings such as axial bearings and/or radial bearings can for example be embodied as slide bearings, ball bearings, spherical roller bearings, etc.
- the necessary installation space for a fixed bearing unit (the fixed bearing unit has in particular a radial bearing and two axial slide bearings) with its combination of for example axial slide bearings with a radial slide bearing is very large as a result of the arrangement, as the internal diameter of the axial bearing is greater than the radial bearing diameter.
- appropriate intermediate bodies are employed to accommodate the bearing components, which are fixed in the housing-bearing block. If the fixed bearing unit is now dispensed with, it is possible to manage without intermediate body and to use the minimal installation space which the radial slide bearings alone require for the housing structure and its optimization.
- the optimization of the linkage of the radial bearings is successful if this is accommodated directly in the housing structure. If no fixed bearing unit is now present, that is this is dispensed with, the function of the two axial slide bearings of the fixed bearing unit can be transferred into the position of the respective shaft ends (shaft end face).
- the shaft has also two shaft ends, in the area of which axial bearings, in particular axial slide bearings, are now positioned. In this position the possibility exists of using the components of the gearbox, such as for example a cover and/or a housing structure (in particular an internal housing structure), for the adaption of the axial bearing.
- the shaft ends are also available for this purpose.
- the first radial bearing is a floating bearing.
- the floating bearing is in particular a slide bearing.
- the thus mounted shaft is thereby rotatably mounted.
- the second radial bearing is a floating bearing.
- the floating bearing is in particular a slide bearing.
- the thus mounted shaft is thereby rotatably mounted.
- the first axial bearing is fixed in a housing of the gearbox.
- the interior of the housing is here in particular formed in such a way that accommodation and fixing can take place in a space-saving manner.
- the second axial bearing is fixed by means of a cover of the housing of the gearbox.
- a smaller installation space can thereby be realized and/or exchange of the second axial bearing facilitated.
- the two radial bearings, the shaft and/or the first axial bearing can also be exchanged.
- the first axial bearing is connected to a first oil sump.
- the oil in the oil sump serves to lubricate the bearing.
- the second axial bearing is connected to a second oil sump.
- the oil in the oil sump serves to lubricate the bearing.
- the first oil sump is connected to the second oil sump in such a way that oil can find its way from the first oil sump to the second oil sump and vice versa.
- oil can be forced out of the first oil sump and reach the second oil sump, and vice versa. This can, for example, occur in the case of a change in load, an emergency stop or during reversing operation of a gearbox.
- this has an axial bearing, which is a reversing axial bearing, wherein this is designed as a displacement pressure bearing.
- the first axial bearing is thus for example a reversing axial bearing.
- An oil sump belonging to the axial bearing can be located in the area of the shaft end face.
- the oil sump compartment thus embodied is in particular enclosed by the housing cover, the shaft end with or without thrust washer and/or a drilled hole in the housing.
- An oil drain positioned at 11 o'clock or 1 o'clock for example limits the oil level of the local oil sump.
- the oil sump has the advantage compared with the pressure oil supply that the gap can always have a 100% oil filling level.
- the reversing load has a time-limited, dynamically oscillating character, the possibility thus exists of not designing the bearing in a stationary manner, but dynamically as a squeeze film damper. A change in load takes place for example on average around every 0.37 sec for an emergency turbine stop.
- the radial expansion of the first radial bearing is smaller than the radial expansion of the first axial bearing. A compact structure can thus be achieved.
- the radial expansion of the second radial bearing is smaller than the radial expansion of the second axial bearing. A compact construction can thus also be achieved.
- the second axial bearing is designed for a greater number of operating hours, in particular double the number of operating hours, than the first axial bearing. After opening of the housing cover the second axial bearing is more readily accessible than the first axial bearing, as the second axial bearing is located directly behind the housing cover. The replacement of a more easily accessible bearing reduces the downtime of the bearing when this is under maintenance.
- the first axial bearing abuts a first shaft end face and/or the second axial bearing abuts a second shaft end face. If the axial bearings are directly abutting, this thus contributes to a compact construction.
- At least one shaft end face is adapted to at least one of the axial bearings by means of a thrust washer. Differences in size between axial bearing and shaft end face can thus be balanced out. Thus if for example the shaft ends are too small, the possibility exists of adapting the thrust washers to the shaft ends, which then function as a counter running surface.
- This method can also be partially implemented, for example by continuing, on the intermediate shaft of a gearbox, to use the wheel as a running surface for the axial bearing, which is then adapted to the internal wall of the housing.
- At least one of the axial bearings is a reversing axial bearing, wherein this is in particular embodied as a displacement pressure bearing. This reduces the complexity of the lubrication.
- a wind gearbox advantageously has a mounting according to at least one of the embodiments described.
- the embodiments can be combined with each other.
- a space-saving gearbox with a mounting of this kind can thus be realized, which for example is of benefit in the confined space conditions in a nacelle of a wind power plant.
- this has an intermediate shaft, wherein this is an intermediate shaft of a two-stage spur gear portion of the wind gearbox.
- a reversing bearing has a lubrication gap of greater than 0.5 mm. If there is oil in this lubrication gap, this can be partially forced out of the gap in the case of a change in load, which has a damping effect.
- a compression time of the reversing bearing is selected which corresponds to a frequency of a change in load.
- the reversing axial bearing is designed as a displacement pressure bearing.
- an oil sump would be provided in the area of at least one of the shaft end faces.
- the oil sump compartment is for example enclosed by the housing cover, a shaft end with thrust washer and/or a drilled hole in the housing.
- the direct pressure oil supply for the axial bearing on the shaft end does not apply.
- the oil sump has the advantage compared with the pressure oil supply that the gap preferably always has a 100% oil filling level.
- the reversing load has a time-limited, dynamically oscillating character, the possibility thus exists of not designing the bearing in a stationary manner, but dynamically as a squeeze film damper.
- the reversing bearing has a large gap (because it is not under load) and consequently upon the occurrence of a reversing load from the normal loading state, a large initial lubrication gap in the order of magnitude of, for example, greater than 0.5 mm.
- the compression time selected is greater than an impact time.
- the time that the bearing requires to overcome the axial play is called the compression time.
- the compression time of the reversing axial bearing accordingly lies in the order of magnitude of the frequency of the change in load.
- the amplitude time from the occurrence of the reversing impact to the next zero-crossing then amounts to, for example, 0.37 sec (impact duration). If, taking account of the inertias and frictional resistances, the compression time of the reversing bearing is greater than the impact duration, no contact with the sliding surfaces takes place.
- FIG. 1 a first mounting with an intermediate shaft
- FIG. 2 a second mounting with an intermediate shaft
- FIG. 3 a torque profile for a gearbox of a wind power plant as a function of the rotational speed.
- FIG. 1 shows, in sectional form, a first wind gearbox 1 , which has a mounting 3 and a gearbox housing 28 .
- the mounting 3 has a floating bearing 10 and a fixed bearing unit with steel adapter 11 .
- the floating bearing 10 is for example a radial slide bearing.
- the fixed bearing unit 11 has a steel adapter, a left-hand axial mounting 13 and a right-hand axial mounting 14 , as well as a radial mounting 12 .
- An intermediate shaft 5 of the gearbox 1 is mounted by means of the mounting 3 .
- the intermediate shaft 5 has a first shaft end 6 , that is a first shaft end area 6 .
- a first shaft end face 8 is located at the first shaft end 6 .
- the floating bearing 10 is located in the area of the first shaft end 6 .
- a second shaft end face 9 is located on the second shaft end 7 .
- the fixed bearing unit 11 is located in the area of the second shaft end 7 . This fixed bearing unit is accessible via a gearbox housing cover 29 .
- Gear elements are located between the first shaft end 6 and the second shaft end 7 .
- a first gear element is toothing 19 integrated into the intermediate shaft 5 .
- a second gear element is a first gear wheel 20 on the intermediate shaft 5 .
- a second gear wheel 21 engages in the toothing 19 .
- the first gear wheel 20 is provided for the transmission of forces to a connection shaft 31 .
- FIG. 1 an intermediate shaft 5 of a two-stage spur gear portion of a wind gearbox 1 , with steel bodies to accommodate the large axial slide bearings 13 and 14 in the fixed bearing unit, is shown on the right.
- the fixed bearing unit can be optimized to the effect that existing gearbox components are used as a counter running surface.
- the gear wheel can be used as a counter running surface.
- this is not possible in the case of all shafts in the spur gear unit, as the toothings do not always enable this due to their size (reason: excessively small pinion teeth).
- the required installation space of axial slide bearings in combination with a radial slide bearing is very large as a result of the arrangement, as the internal diameter of the axial bearing is greater than the radial bearing diameter.
- the result is that the radial bearings with their low design height do not lead to the desired installation space advantages.
- the aim is to manage without the intermediate bodies and to use the minimal installation space, which the radial slide bearings alone require, for the housing structure and its optimization.
- the optimization of the linkage of the radial bearings is successful if these can be accommodated directly in the housing structure.
- the fixed bearing unit can also be improved to the effect that existing gearbox components are used as a counter running surface.
- the gear wheel 20 can be used as a counter running surface.
- FIG. 2 shows, in sectional form, a further wind gearbox 2 , wherein the principle of an axial slide bearing on the shaft ends with oil sump is shown.
- An intermediate shaft 5 which has a first bearing block 17 for a first radial bearing 15 on the first shaft end 6 is shown.
- On the second shaft end 7 is a second bearing block 18 for a second radial bearing 16 .
- a first axial bearing 22 with a first thrust washer 24 is located at the first shaft end face 8 .
- a first oil sump 32 for lubrication of the first axial bearing 22 is located in a first oil sump compartment 26 .
- a second axial bearing 23 with a radial expansion 34 is located at the second shaft end face 9 .
- a second thrust washer 25 is located between the second axial bearing 23 and the second shaft end face 9 .
- a second oil sump 33 for lubrication of the second axial bearing 23 is located in a second oil sump compartment 27 .
- the second axial bearing 23 is fixed by the gearbox housing cover 30 .
- the mounting 4 according to FIG. 2 has the first radial bearing 15 and the first axial bearing 22 at or on the first shaft end 6 .
- the mounting 4 has the second radial bearing 16 and the second axial bearing 23 at or on the second shaft end 7 .
- the representation according to FIG. 3 shows a torque profile for a gearbox of a wind power plant depending on the rotational speed in particular the progress of rotational speed and torque of an emergency stop of a wind power plant.
- the figure shows how with an emergency stop the torque value (Torque) 35 fluctuates around a value of zero. This fluctuation places a stress on the mounting of the gearbox employed, wherein in particular the thickness of a lubrication gap and the lubricant located therein is to be designed to be such that the lubrication gap does not disappear as a result of the fluctuation or oscillation around the value of zero, so that lubrication with the lubricant can take place at all times.
- the actual rotational speed value (Rot. Speed) 37 is shown too.
- the nominal rotational speed value (Rot. Speed (Nom)) 38 and the nominal torque value (Torque (Nom)) 36 are shown in addition.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Sustainable Energy (AREA)
- Combustion & Propulsion (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- General Details Of Gearings (AREA)
- Sliding-Contact Bearings (AREA)
- Wind Motors (AREA)
Abstract
Description
-
- less installation space for the axial mounting;
- fewer components;
- cost reduction through lower usage of material and/or
- optimization of the housing structure in the case of lower usage of material.
-
- sump lubrication for the axial bearing;
- designing of the reversing axial bearing as a squeeze film damper (displacement pressure buildup) and/or
- dispensing with pressure lubrication for the reversing bearing.
Claims (16)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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DE102017209217.3 | 2017-05-31 | ||
DE102017209217.3A DE102017209217A1 (en) | 2017-05-31 | 2017-05-31 | Storage of an intermediate shaft, in particular a wind gear |
PCT/EP2018/064052 WO2018219939A1 (en) | 2017-05-31 | 2018-05-29 | Mounting of an intermediate shaft, in particular of a wind gearbox |
Publications (2)
Publication Number | Publication Date |
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US20200088173A1 US20200088173A1 (en) | 2020-03-19 |
US11168672B2 true US11168672B2 (en) | 2021-11-09 |
Family
ID=62567619
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US16/616,290 Active 2038-08-03 US11168672B2 (en) | 2017-05-31 | 2018-05-29 | Mounting of an intermediate shaft in particular of a wind gearbox |
Country Status (6)
Country | Link |
---|---|
US (1) | US11168672B2 (en) |
EP (1) | EP3574223B1 (en) |
CN (1) | CN110621892B (en) |
DE (1) | DE102017209217A1 (en) |
ES (1) | ES2893453T3 (en) |
WO (1) | WO2018219939A1 (en) |
Citations (16)
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DE3827741A1 (en) * | 1987-11-23 | 1989-06-01 | Hermsdorf Keramik Veb | Axial-radial slide bearing for sensor systems in ignition distributors for spark ignition engines |
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DE20218170U1 (en) | 2002-07-15 | 2003-08-28 | Minebea Co Ltd | Hydrodynamic bearing, especially for the spindle motor of a hard disk drive, has a design that ensures as small a power loss as possible, high bearing rigidity and a long service life |
US6939046B2 (en) * | 2002-07-15 | 2005-09-06 | Minebea Co., Ltd. | Hydrodynamic bearing, spindle motor and hard disk drive |
US20060078241A1 (en) | 2004-10-07 | 2006-04-13 | Keven Moehring | Bearing element |
JP2008106894A (en) | 2006-10-27 | 2008-05-08 | Mitsubishi Heavy Ind Ltd | Backlash eliminator |
DE602004007836T2 (en) | 2003-02-18 | 2008-05-21 | General Electric Co. | Transmission for wind turbine |
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- 2018-05-29 CN CN201880031085.6A patent/CN110621892B/en active Active
- 2018-05-29 EP EP18730272.4A patent/EP3574223B1/en active Active
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Also Published As
Publication number | Publication date |
---|---|
ES2893453T3 (en) | 2022-02-09 |
WO2018219939A1 (en) | 2018-12-06 |
CN110621892A (en) | 2019-12-27 |
EP3574223B1 (en) | 2021-09-22 |
CN110621892B (en) | 2021-10-22 |
DE102017209217A1 (en) | 2018-12-06 |
EP3574223A1 (en) | 2019-12-04 |
US20200088173A1 (en) | 2020-03-19 |
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